CN102252114A - Flow path switching valve - Google Patents
Flow path switching valve Download PDFInfo
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- CN102252114A CN102252114A CN2011101091837A CN201110109183A CN102252114A CN 102252114 A CN102252114 A CN 102252114A CN 2011101091837 A CN2011101091837 A CN 2011101091837A CN 201110109183 A CN201110109183 A CN 201110109183A CN 102252114 A CN102252114 A CN 102252114A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
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- General Engineering & Computer Science (AREA)
- Fluid-Driven Valves (AREA)
- Multiple-Way Valves (AREA)
Abstract
The invention relates to a flow path switching valve. The flow path switching valve 10 uses two pistons 2, 2 to divide a valve shell 1 into a primary valve chamber 11A and the secondary valve chambers 12A, 12A on two sides. One secondary valve chamber 12A on one side is decompressed and a pressure difference between this secondary valve chamber and a refrigerant pressure in the primary valve chamber 11A is used to drive the piston 2 and a primary valve core 5 to move, convert the flow path of the refrigerant in circulation and guarantee the service durability of the piston 2. A pressure equalizing path is provided in the center of the piston 2, and a secondary valve 25 is disposed in the pressure equalizing path. When the piston 2 is moved toward a cap 12, the secondary valve 25 closes an opening of an exhaust path 12a at a secondary valve seat, and opens the pressure equalizing path.
Description
Technical field
The present invention relates to be used for the refrigeration cycle of air conditioner etc. and the runner changing valve of conversion refrigerant flow path.
Background technique
In the past, the runner of refrigeration agent, thereby convertible cooling operation and heat running by the conversion refrigeration cycle in air conditioner etc.In this refrigeration cycle, two heat exchangers that use compressor, use as condenser or vaporizer, change the runner changing valve of the runner of the flow of refrigerant between these compressors and two heat exchangers.
As this runner changing valve, the disclosed technology of TOHKEMY 2009-68695 communique (patent documentation 1) is for example arranged.This runner changing valve holds the piston main body that has connected two pistons and main valve plug in the valve casing (valve body) of tubular, main valve plug is slided and the runner of the refrigeration agent that conversion is flowed in a plurality of pipe arrangements at axial direction with respect to the valve seat in the valve casing.In conversion during this runner, utilize the differential pressure of pressure of refrigeration agent of secondary valve chamber in the outside of the pressure of refrigeration agent of main valve chamber of two piston spaces and piston that piston main body is moved.
In addition, the runner conversion threshold of this patent documentation 1 is when moving piston main body, by second spool (ball) that is configured on the piston is contacted with valve seat on the end cover that is arranged on valve casing, obturation is arranged on the pump drainage tracheae on this valve seat, press thereby the secondary valve chamber of on high-tension side main valve chamber and base pressure side is become all, act on the differential pressure on the liner of piston with reduction.Thus, even be ultrahigh pressure at fluid, particularly as CO
2Under the situation of the refrigeration agent of such ultrahigh pressure, also can obtain the durability of piston.
The prior art document
Patent documentation 1: TOHKEMY 2009-68695 communique
In the runner changing valve of above-mentioned patent documentation 1, around the liner of piston, possess the rake of ring-type, its sectional shape becomes the shape that tilts to the direction near the inner face of valve casing gradually along with towards the end of valve casing.And constitute: after the main valve chamber side is to utilize the inaccessible pump drainage tracheae of second spool under the state of high pressure and the state that secondary valve chamber is low pressure, main valve chamber and secondary valve chamber reach when all pressing, and the high-pressure refrigerant of main valve chamber side escapes to secondary valve chamber between the inner face of the rake of liner and valve casing.Therefore, main valve chamber and secondary valve chamber reach successfully all that to press be difficult, and the leeway of improvement is still arranged.
Summary of the invention
The present invention is the technological scheme that proposes in order to solve aforesaid problem points, its purpose is to provide a kind of runner changing valve, in the valve casing of tubular, connect and hold two pistons and main valve plug, utilize the differential pressure of refrigeration agent of the secondary valve chamber in the main valve chamber of piston inboard and the piston outside, make main valve plug with respect in the runner changing valve of valve seat slip with conversion runner of mobile refrigeration agent in a plurality of pipe arrangements, main valve chamber and secondary valve chamber are reached all reliably press, obtain the durability of piston.
The runner changing valve of scheme one, in the valve casing of tubular, accommodate on the axis that is configured in this valve casing and interconnective two pistons, utilize above-mentioned two pistons to be separated into the main valve chamber of the central part that connects the high pressure side pipe arrangement in the above-mentioned valve casing, two secondary valve chambers with the both sides of this main valve chamber, to be configured in the above-mentioned main valve chamber with the main valve seat that two conversion side lines are connected with the low voltage side pipe arrangement, and will with respect to above-mentioned main valve seat on above-mentioned axial direction slidably main valve plug dispose with above-mentioned piston with being connected, by high-pressure refrigerant being imported the either party of above-mentioned two secondary valve chambers, and the secondary valve chamber of the opposing party is reduced pressure, thereby utilizing in this post-decompression secondary valve chamber makes above-mentioned piston and main valve plug to this pair valve chamber side shifting with the interior differential pressure of above-mentioned main valve chamber, and the recess that utilizes this main valve plug make above-mentioned low voltage side pipe arrangement select a ground with above-mentioned two the conversion side lines either party be communicated with, and be communicated with above-mentioned high pressure side pipe arrangement by the conversion side line of above-mentioned main valve chamber with the opposing party, with flowing of conversion refrigeration agent, this runner changing valve is characterised in that, two ends in above-mentioned valve casing inside form auxiliary-seat portion, this auxiliary-seat portion is side-prominent to above-mentioned main valve chamber, and the pump drainage gas passage that makes the passage that becomes above-mentioned refrigeration agent is to the valve casing inner opening, on above-mentioned each piston and with above-mentioned auxiliary-seat portion corresponding above-mentioned axis on form the equal pressure passageway that above-mentioned main valve chamber and above-mentioned secondary valve chamber are communicated with, and in this equal pressure passageway, set secondary valve, utilize this pair valve to change the conducting and the obturation of this equal pressure passageway moving of above-mentioned axial direction with respect to this equal pressure passageway, at above-mentioned piston when above-mentioned post-decompression secondary valve chamber side shifting finishes, the above-mentioned secondary valve obturation of this piston should pair valve chamber side the opening of above-mentioned auxiliary-seat portion, thereby and pass through this auxiliary-seat portion and the above-mentioned equal pressure passageway of this pair valve butt conducting, and make above-mentioned post-decompression secondary valve chamber and above-mentioned main valve chamber reach all pressures by means of this equal pressure passageway.
The runner changing valve of scheme two is on the basis of scheme one described runner changing valve, it is characterized in that, above-mentioned piston has the liner that contacts with the inner face of above-mentioned valve casing, form the rake that extends with ring-type to the central part side of valve casing in the periphery of this liner, this rake for its sectional shape along move closer to the shape that tilts in the direction of the inner face of valve casing along with central part towards above-mentioned valve casing.
Effect of the present invention is as follows.
Runner changing valve according to scheme one, since at piston when post-decompression secondary valve chamber side shifting finishes, the opening of the auxiliary-seat portion of the inaccessible secondary valve chamber side of secondary valve of piston, therefore stop the decompression of this pair valve chamber, and auxiliary-seat portion and secondary valve butt and the equal pressure passageway of conducting, refrigeration agent flows to secondary valve chamber by equal pressure passageway from main valve chamber, thereby carries out all pressures of main valve chamber and secondary valve chamber smoothly.Like this, the sealed member applied pressure load of the piston when not mobile disappears, and can prevent the creep strain of sealed member.In addition, can also prevent to constitute the stress deformation of the parts of piston.Therefore, as using CO
2The runner changing valve of the ultrahigh pressure refrigeration agent that refrigeration agent is such is particularly suitable for.
Runner changing valve according to scheme two, except the effect of scheme one, when secondary valve chamber is depressurized between the main valve chamber of this post-decompression secondary valve chamber and high pressure in the piston, because playing a role, the high-pressure refrigerant of main valve chamber side make the rake of liner by being pressed in the valve casing inner face side, therefore can utilize the main valve chamber of airtight reliably decompression attached valve chamber in back of this liner and high pressure, it is reliable that the shift action of piston and main valve plug becomes.
Description of drawings
Fig. 1 is the figure of runner changing valve, control valve and the refrigeration cycle of expression embodiments of the present invention.
Fig. 2 is the major component sectional view of the runner changing valve of mode of execution.
Fig. 3 is the major component Action Specification figure of the runner changing valve of mode of execution.
Fig. 4 is the major component sectional view of the control valve of mode of execution.
Fig. 5 is the time diagram of driving example of the control valve of expression mode of execution.
Fig. 6 is other routine major component sectional views of piston of the runner changing valve of expression mode of execution.
Among the figure:
The 1-valve casing, 2-piston, 3-connected element, 4-main valve seat, 5-main valve plug, 5A-main valve recess, the 11-cylindrical part, 11A-main valve chamber, 12-cap, the secondary valve chamber of 12A-, 12-main valve seat, 12a-pump drainage gas passage, 122-auxiliary-seat portion, 13a-E type conjugation tube, 13b-S shape conjugation tube, 13c-C type conjugation tube.13d-D type conjugation tube, the secondary valve of 25-, 21a-hole (all pressure passageway), 22a-hole (all pressure passageway), 23a-hole (all pressure passageway), 24a-hole (all pressure passageway), 10-runner changing valve, 20-control valve, 30-compressor, the 40-outdoor unit, 50-indoor set, 60-throttling arrangement, L1-axis.
Embodiment
Below, embodiments of the present invention are described.Fig. 1 is the figure of runner changing valve, control valve and the refrigeration cycle of expression mode of execution.The runner changing valve 10 of this mode of execution is a four-port conversion value, and this runner changing valve 10 utilizes pipe arrangement to be connected with control valve 20.In runner changing valve 10, valve casing 1 is a cylindrical shape, is made of the cylindrical part 11 of drum and two caps 12,12 of circular plate shape.Cap 12,12 is installed on the cylindrical part 11 by welding etc., so that the end of inaccessible cylindrical part 11 respectively, the central shaft of cylindrical part 11 and cap 12,12 becomes the axis L1 of valve casing 1.Cylindrical part 11 sides at cap 12,12 are formed with slim circular depressions 121.
The axis L1 that in valve casing 1, accommodates at valve casing 1 configuration and by connected element 3 interconnective two pistons 2,2.Thus, the inside of the valve casing 1 that is made of the circular depressions 121,121 of the inboard of cylindrical part 11 and cap 12,12 is separated into the main valve chamber 11A of central authorities and two secondary valve chamber 12A, 12A of main valve chamber 11A both sides by two pistons 2,2.
Intermediate portion in main valve chamber 11A is equipped with main valve seat 4, is equipped with the main valve plug 5 that slides along the axis L1 direction of valve casing 1 on main valve seat 4.On main valve seat 4 and along the axis L1 direction of valve casing 1, form E type mouth 4a, S type mouth 4b and C type mouth 4c point-blank side by side, on these E type mouths 4a, S type mouth 4b and C type mouth 4c, be separately installed with E type conjugation tube 13a, S type conjugation tube 13b, C type conjugation tube 13c.In addition, be formed with D type mouth 11a, on this D type mouth 11a, D type conjugation tube 13d be installed in the position relative of the intermediate portion of cylindrical part 11 with main valve seat 4.In addition, E type conjugation tube 13a and C type conjugation tube 13c are equivalent to " conversion side line ", and S type conjugation tube 13b is equivalent to " low voltage side pipe arrangement ", and D type conjugation tube 13d is equivalent to " high pressure side pipe arrangement ".Thus, be connected with D type conjugation tube 13d as the high pressure side pipe arrangement at main valve chamber 11A, main valve seat 4 is connected with two conversion side lines with the low voltage side pipe arrangement.
Central authorities at connected element 3 are formed with spool embedding hole 3a, are formed with perforation 3b, 3c in its both sides.3a is embedded in main valve plug 5 at the spool embedding hole.This main valve plug 5 has with gap a little in axis L direction with respect to connected element 3 and is held.And main valve plug 5 then slides on main valve seat 4 with connected element 3 when piston 2,2 moves in linkage, and stops in the position, the left and right sides that is predetermined.
Main valve plug 5 is that the sheet metal 51 of cup-shaped is inserted the member that is shaped with resinous parts 52, forms main valve recess 5A by the inboard of this sheet metal 51.And main valve plug 5 utilizes main valve recess 5A that S type mouth 4b and E type mouth 4a are communicated with at the end position in the left side of Fig. 1.At this moment, C type mouth 4c mainly is communicated with D type mouth 11a by perforation 3c at main valve chamber 11A.In addition, main valve plug 5 utilizes main valve recess 5A that S type mouth 4b and C type mouth 4c are communicated with in the right-hand end position of Fig. 1.At this moment, E type mouth 4a is main in main valve chamber 11A is communicated with D type mouth 11a by perforation 3b.
S type conjugation tube 13b is connected with the suction port of compressor 30 by low-voltage tube 14a, and D type conjugation tube 13d is connected with the exhaust port of compressor 30 by high-voltage tube 14b.C type conjugation tube 13c is connected with outdoor unit 40 by conduit 14c, and E type conjugation tube 13a is connected with indoor set 50 by conduit 14d.Outdoor unit 40 is got involved throttling arrangement 60 with indoor set 50 and is connected by conduit 14e.The path that constitutes by this C type conjugation tube 13c, outdoor unit 40, throttling arrangement 60, indoor set 50 and E type conjugation tube 13a certainly and constitute refrigeration cycle by the path that constitutes that constitutes from S type conjugation tube 13b, compressor 30 and D type conjugation tube 13d.
And, as described later, by the position of the main valve plug 5 of control valve 20 conversion runner changing valves 10.High-pressure refrigerant with compressor 30 compressions flows in the main valve chamber 11A by D type mouth 11a from D type conjugation tube 13d, and under the cooling operation state of Fig. 1, high-pressure refrigerant flows into outdoor unit 40 from C type mouth 4c.And, heating under the operating condition behind conversion main valve plug 5, high-pressure refrigerant flows into indoor set 50 from E type mouth 4a.Promptly, when cooling operation, the refrigeration agent of discharging from compressor 30 circulates through C type conjugation tube 13c → outdoor unit 40 → throttling arrangement 60 → indoor set 50 → E type conjugation tube 13a, outdoor unit 40 as condenser (condenser) work, indoor set 50 works as vaporizer (evaporator), freeze.In addition, heating when running, refrigeration agent circulates on the contrary, indoor set 50 as condenser work, outdoor unit 40 works as vaporizer, heat.In addition, " C ", " E " of C type mouth 4c and E type mouth 4a are to be the additional title of benchmark with the cooling operation.
The auxiliary-seat portion 122 of in the central authorities (axis L1) that are formed with on each cap 12,12 in circular depressions 121, giving prominence to the inside.In addition, on cap 12,12, be formed with the pump drainage gas passage 12a that penetrates into the end 122a of auxiliary-seat portion 122 from sidepiece, on this pump drainage gas passage 12a, 12a, be connected with conduit 15f, 15g respectively.
In Fig. 1, control valve 20 possesses two electromagnetic drivers.This control valve 20 has block valve casing 61, is fixed with two plunger housings 62,62 airtightly on this valve casing 61, and is fixed with attractor 63,63 airtightly in the end of plunger housing 62,62.And, be equipped with plunger 65 in the inside of plunger housing 62,62.Peripheral part at attractor 63,63 and plunger housing 62,62 is provided with the electromagnetic coil 72,72 that is wound on the coil carrier 71,71.And, utilizing the excitation of electromagnetic coil 72, the inner side end of attractor 63 becomes the magnetic adsorption plane of relative plunger 65.
High pressure conjugation tube 64d, low pressure conjugation tube 64b and two conversion conjugation tube 64a, 64c are installed on valve casing 61.High pressure conjugation tube 64d is connected with the D type conjugation tube 13d (high pressure side) of four-port conversion value 10 by conduit 14f, and low pressure conjugation tube 64d is connected with the S type conjugation tube 13b (low voltage side) of four-port conversion value 10 by conduit 14g.In addition, conversion conjugation tube 64a, 64c are connected with conduit 15f, the 15g of four-port conversion value 10 respectively by conduit 14h, 14i.And, can also constitute high pressure conjugation tube 64d, low pressure conjugation tube 64b, conversion conjugation tube 64a, 64c and conduit 14f, 14g, 14h, 14i respectively with identical parts.
Fig. 4 is the sectional view of detailed structure of the major component of expression control valve 20.Be formed with control valve chamber 61A cylindraceous on valve casing 61, above-mentioned plunger housing 62,62 relative axis L2 embed the two ends of this control valve chamber 61A coaxially.Plunger housing 62,62 is a drum.In addition, in control valve chamber 61A, between plunger housing 62,62, control valve seat 66 is installed, possesses the control spool 67 that slides in the axis L2 of plunger housing 62,62 direction on the top of this control valve seat 66.On control valve seat 66 upper edge axis L2 directions and straight line, be formed with control transformation mouth 61a, control low pressure port 61b and control transformation mouth 61c side by side.Above-mentioned conversion conjugation tube 64a, low pressure conjugation tube 64b, conversion conjugation tube 64c are installed on these control transformation mouths 61a, control low pressure port 61b and control transformation mouth 61c.And, be formed with control high-pressure mouth 61d in the position with control valve seat 66 opposition sides of the intermediate portion of valve casing 61, above-mentioned high pressure conjugation tube 64d is installed on this control high-pressure mouth 61d.
In plunger housing 62,62, be equipped with above-mentioned plunger 65 in the mode that connects control valve chamber 61A.Plunger 65 is for roughly cylindric, has the little minor diameter 651 of the diameter of central authorities and with the inner face coupling of plunger housing 62,62 and in the big large-diameter portion 652,652 of diameter of the both sides of minor diameter.In addition, plunger 65 has with axis L2 and has been cut a part of D shape cutting surface 65a abreast, and 65a is relative with control valve seat 66 for this D shape cutting surface.Form spool retaining hole 65b in the central authorities of minor diameter 651 from D shape cutting surface 65a side utilization cutting, and be formed with from this spool retaining hole 65b and be communicated to intercommunicating pore 65c with D shape cutting surface 65a opposition side.In spool retaining hole 65b, be equipped with control spool 67 and helical spring 68.
On control spool 67, be formed with control recess 67a in control valve seat 66 sides.And control spool 67 utilizes control recess 67a that control transformation mouth 61a and control low pressure port 61b are communicated with at the end position in the left side of Fig. 4.At this moment, control transformation mouth 61c is by means of being communicated with control high-pressure mouth 61d around control valve chamber 61A and the minor diameter 651.In addition, control spool 67 utilizes control recess 67a that control transformation mouth 61c and control low pressure port 61b are communicated with at the end position on the right side of Fig. 4.At this moment, control transformation mouth 61a is by means of being communicated with control high-pressure mouth 61d around control valve chamber 61A and the minor diameter 651.
Like this, control valve 20 utilizes energising to electromagnetic coil 72 to make plunger 65 be attracted son 63 absorption and makes control spool 67 carry out straight line motion along axis L2.Thus, conversion is supplied with high-pressure refrigerant and state that the secondary valve chamber 12A on right side is reduced pressure and the state supplying with high-pressure refrigerant and the secondary valve chamber 12A in left side is reduced pressure to the secondary valve chamber 12A on the right side of four-port conversion value 10 from control transformation mouth 61c from control transformation mouth 61a to the secondary valve chamber 12A in the left side of four-port conversion value 10, the runner of conversion refrigeration cycle.
And control spool 67 by being pressed on the control valve seat 663, can improve the sealing between control spool 67 and the control valve seat 66 by helical spring 68.In addition, control valve seat 66 is metal parts, and control spool 67 is resinous parts.Therefore, utilize the resin plasticity of control spool 67 to can further improve the sealing of controlling between spool 67 and the control valve seat 66.Using ultrahigh pressure CO
2Under the situation as refrigeration agent, this high leak tightness is effective especially.
Fig. 5 is the time diagram of expression to the example of two electromagnetic coils, 72,72 energising controls.In Fig. 1, the electromagnetic coil 72 in left side is made as " loop A ", the electromagnetic coil 72 on right side is made as " coil B ".Shown in Fig. 5 (A), when loop A is switched on (during connection), making coil B is non-energising (disconnection).Thus, the position of control spool 67 is positioned at left side (electromagnetic coil 72 sides after the energising).And control high-pressure mouth 61d and control transformation mouth 61c are communicated with, and control transformation mouth 61a and control low pressure port 61b are communicated with.Even loop A is non-energising (disconnection), the position of control spool 67 also maintains the original state.Secondly, be under the state of non-energising in loop A, if to coil B energising (connection), the position of then controlling spool 67 is positioned at right side (electromagnetic coil 72 sides after the energising).And control high-pressure mouth 61d and control transformation mouth 61a are communicated with, and control transformation mouth 61c and control low pressure port 61b are communicated with.Even coil B is non-energising (disconnection), the position of control spool 67 also maintains the original state.And, shown in Fig. 5 (B), carry out the energising of electromagnetic coil 72 and the position of conversion and control spool 67, then,, can also apply sustaining voltage, and sustaining voltage is flowed up to transition period next time.
The control valve 20 of this mode of execution is at two plunger housings 62 that are co-axially mounted on the valve casing 61, be equipped with the plunger 65 of retentive control spool 67 in 62, control spool 67 is free to slide in axis L2 direction with plunger 65 on the control valve seat 66 that connects with a plurality of joints, at plunger housing 62,62 end is fixed with attractor 63 airtightly, 63, and at attractor 63,63 and plunger housing 62,62 peripheral part is provided with electromagnetic coil 72 respectively, 72, by to this electromagnetic coil 72,72 either party switches on and makes the opposing party is non-energising, thereby the excitation of utilizing the electromagnetic coil 72 after the energising makes attractor 63 absorption plungers 65, utilizes the flowing of refrigeration agent of a plurality of pipe arrangements of control spool 67 conversions.
Control valve 20 ratios such as the disclosed control valve of Japanese kokai publication hei 8-170865 communique of this mode of execution are good.This existing control valve makes the control spool move to a side by the energising to an electromagnetic driver, cuts off the energising to electromagnetic driver, and utilizes the active force of spring that the control spool is moved to the opposing party.Thus, owing to act on the head pressure of the refrigeration agent of control spool,, must strengthen the driving force and the elastic force of electromagnetic driver for driving this control spool.In addition, elastic force hinders the power that electromagnetic driver produces, and reduces the efficient of attraction force.
Relative therewith, in the control valve 20 of mode of execution, there is not spring, possess two relative electromagnetic drivers, drive these two electromagnetic drivers by mutual conversion ground, thereby there is not the efficient that elastic force causes to reduce, the control spool of can be enough small-sized, cheap electromagnetic driver driving action head pressure.In addition, produce under the state of differential pressure on the control spool, even disconnect the energising of coil, the position of control spool can not change yet, and therefore can realize no-voltage bolt lock mechanism, can improve energy saving.And, in existing structure, press owing to light current under the situation about reducing, owing to the balance with elastic force produces magnetosonic, but in the control valve 20 of mode of execution, owing to not having spring thereby can reducing the generation of magnetosonic in adsorption force.
Like this, control valve 20 makes the high-pressure refrigerant that flows into from high pressure conjugation tube 64d flow out from conversion conjugation tube 64a or conversion conjugation tube 64c, and this high-pressure refrigerant supplies to the secondary valve chamber 12A in left side or the secondary valve chamber 12A on right side in four-port conversion value 10.At this moment, the secondary valve chamber 12A in the secondary valve chamber 12A on the right side of four-port conversion value 10 or left side is by means of low pressure conjugation tube 64b and low voltage side conducting.Thus, utilize control valve 20, in four-port conversion value 10, the secondary valve chamber 12A that secondary valve chamber 12A of the side becomes high pressure and the opposing party is depressurized.And, main valve chamber 11A is always supplied with high-pressure refrigerant.Therefore, the differential pressure of the pressure of the pressure of the secondary valve chamber 12A after being depressurized and the high pressure of main valve chamber 11A is applied on the piston 2 of post-decompression secondary valve chamber 12A side, mainly, piston 2 and main valve plug 5 utilize this differential pressure to post-decompression secondary valve chamber 12A side shifting, and the position of this main valve plug 5 is changed.
Here, each piston 2 becomes the reflection symmetrical structure in Fig. 1.Below, be example explanation detailed structure based on Fig. 2 with the piston 2 in left side.Piston 2 possesses the fixed disc 21 that is fixed on the connected element 3, leaf spring 22, liner 23, discoideus locking plate 24, secondary valve 25 and helical spring 26, and these parts are the center arranged coaxial with axis L1.
Like this, leaf spring 22 and liner 23 are made roughly the same shape, and leaf spring 22 is configured in the inboard of liner 23, are clipped between fixed disc 21 and the locking plate 24 with the part of plectane portion 221,231, and are fixed respectively.With regard to leaf spring 22, the end of a side of leaving from plectane portion 221 of the afterburning portion 222 of tilting is by the rake 232 free resiliently deformables of liner 23, so that this rake 232 is in the inner face sliding contact of valve casing 1.In addition, leaf spring 22 produces the rake 232 that makes the liner 23 that leaves from the inner face of valve casing 1 elastic recovering force to the inner face reinforcing of valve casing 1.And leaf spring 22 is under the state of the valve casing 1 of packing into (cylindrical part 11), and the rake 232 of liner 23 is pushed in the end of a side of leaving from plectane portion 221 of the afterburning portion 222 of tilting to the inner face of valve casing 1.Thus, the high-pressure refrigerant in the relative main valve plug 11A, liner 23 seals reliably at the inner peripheral surface of cylindrical part 11.
In each piston 2, be formed with circular hole 21a, 22a, 23a and 24a respectively at the center of fixed disc 21, leaf spring 22, liner 23 and locking plate 24.And, being formed with circular hole 3d in fixed disc 21 sides of connected element 3, the hole 3d of this connected element 3 is communicated with above-mentioned perforation 3b (being the 3c that bores a hole on the right side) by passage 3e.Wherein, the hole 22a of the hole 3d of connected element 3, the hole 21a of fixed disc 21, leaf spring 22 and the hole 23a of liner 23 are roughly the same diameter, and the hole 24a of locking plate 24 is than the little diameter of above-mentioned each diameter.These holes 21a, 22a, 23a, 24a and 3d constitute " all pressure passageway ", leave the compartment of terrain with its periphery and set secondary valve 25 in this hole 21a, 22a, 23a, 24a and 3d.
The effect of this pair valve 25 is as follows.Low pressure is imported secondary valve chamber 12A of the side, be accompanied by the pressure difference that produces main valve chamber 11A and secondary valve chamber 12A, the piston 2 whole beginnings that comprise secondary valve 25 are moved to the secondary valve chamber 12A of low voltage side (cap 12), when locking plate 24 during with cap 12 butts then piston 2 stop.In the moving process of this piston 2, the end of at first secondary valve 25 (minor diameter 252) and auxiliary-seat portion 122 butts.At this moment, be arranged on pump drainage gas passage 12a among the secondary valve chamber 12A by obturation.Behind the end and auxiliary-seat portion 122 butts of secondary valve 25, the active force that the pressure difference of main valve chamber 11A and secondary valve chamber 12A overcomes helical spring 26 can make piston 2 be moved further, and continues to move to the locking plate 24 that constitutes piston 2 and is connected on the cap 12.At this moving section, owing to always produce the gap between the step end face 25a of auxiliary-seat 25 and locking plate 24, so refrigeration agent flows thereby is tending towards near all pressing to secondary valve chamber 12A from main valve chamber 11A by this gap.Piston 2 reaches the moment of all pressing at main valve chamber 11A and secondary valve chamber 12A, is still in the position of the power that pushes back that maintenance produces by helical spring 26 and piston 2 and the equilibrium of forces such as frictional force in the interior week of cylindrical part 11.And, under this state, if the secondary valve chamber 12A of opposition side is depressurized, piston 2 leaves from cap 12, then utilize under the active force and valve seat 122 state of contact of helical spring 26 at secondary valve 25, locking plate 24 is connected on the step end face 25a, then, proceeds to comprise the moving of piston 2 of secondary valve 25.
Fig. 3 is the figure that the effect of the equal pressure passageway that is made of secondary valve 25 and hole 21a, 22a, 23a, 24a and 3d is described.Fig. 3 (A) is the state after secondary valve 25 leaves from auxiliary-seat portion 122, moves to the process on right side or main valve plug 5 moves to the left side from the center side of valve casing 1 process corresponding to main valve plug in Fig. 15.At this moment, the step end face 25a of secondary valve 25 is connected on the locking plate 24, the conducting of the hole 21a of the hole 24a of blocking locking plate 24 and the hole 23a of liner 23 and fixed disc 21.Be equal pressure passageway by the state of obturation.
Fig. 3 (B) is connected to the state of the above-mentioned Fig. 2 in the auxiliary-seat portion 122 corresponding to secondary valve 25.At this moment, the pump drainage gas passage 12a of the inaccessible auxiliary-seat of the minor diameter 252 of secondary valve 25 portion 122, and locking plate 24 leaves the hole 21a of the hole 24a of locking plate 24, the hole 23a of liner 23, fixed disc 21 and the hole 3d conducting of connected element 3 from the step end face 25a of secondary valve 25.Be the state that equal pressure passageway is switched on.Thus, shown in dashed lines arrow among Fig. 3 (B) like that, hole 21a, the hole 22a of leaf spring 22, the hole 23a of liner 23 and the hole 24a of locking plate 24 of perforation 3b (Fig. 2), the passage 3e of the high-pressure refrigerant in the main valve chamber 11A by connected element 3, hole 3d, fixed disc 21 flow in the secondary valve chamber 12A.And because the pump drainage gas passage 12a of inaccessible auxiliary-seat portion 122, so the pressure of main valve chamber 11A and secondary valve chamber 12A is equal pressures, and the inflow of this refrigeration agent stops.
Like this, owing to carry out all pressures of main valve chamber 11A and secondary valve chamber 12A rapidly, therefore can transfer to the state that refrigerant pressure can not exert an influence to liner 23 rapidly by means of equal pressure passageway.In addition, in this embodiment, the rake 232 of liner 23 extends to the center side of cylindrical part 11 from the outer rim of plectane portion 231, and its sectional shape tilts in the direction of the inner face that moves closer to valve casing 1 along with the center side towards valve casing 1, therefore can keep the high pressure of main valve chamber 11A reliably.
Fig. 6 represents other mode of executions of piston, for the element annotation same-sign identical with Fig. 2 and omit its explanation.This piston 2 ' is discoideus locking plate 27 to be fixed on the connected element 3 and to embed in the periphery of locking plate 27 member that has at the liner 28 of the ring-type of the inner face sliding contact of cylindrical part 11.In addition, be formed with at the center of locking plate 27 with the large-diameter portion 251 corresponding macropore 27a of secondary valve 25 and with minor diameter 252 corresponding aperture 27b, in this macropore 27a and aperture 27b, leave and set secondary valve 25 with gap.This macropore 27a and aperture 27b constitute " all pressure passageway ".And if secondary valve 25 and auxiliary-seat portion 122 butts, locking plate 24 moves to and cap 12 butts, and then in this moving process, the end face on the border of macropore 27a and aperture 27b leaves from the step end face 25a of secondary valve 25 and makes above-mentioned equal pressure passageway be on state.And if locking plate 27 leaves cap 27 from this state, then locking plate 27 and step end face 25a butt make above-mentioned equal pressure passageway be in blocked state.The effect of this pair valve 25 and equal pressure passageway and above-mentioned mode of execution are same.
Above-mentioned mode of execution is effective especially under the situation as the high carbon dioxide of refrigeration agent (fluid) working pressure, but also can use HCFC (HCFC) or HFC various refrigeration agents such as (hydrogen fluorohydrocarbons).In addition, in the present invention,, except above-mentioned mode of execution, also can form spherically,, also can replace it and use leaf spring about helical spring 26 to secondary 25 reinforcings about secondary valve 25.
In addition, above-mentioned mode of execution is only represented representational mode of the present invention, and the present invention is not limited to mode of execution.Various distortion and implementing in addition in the scope that does not break away from main points of the present invention promptly.
Claims (2)
1. runner changing valve, in the valve casing of tubular, accommodate on the axis that is configured in this valve casing and interconnective two pistons, utilize above-mentioned two pistons to be separated into the main valve chamber of the central part that connects the high pressure side pipe arrangement in the above-mentioned valve casing, two secondary valve chambers with the both sides of this main valve chamber, to be configured in the above-mentioned main valve chamber with the main valve seat that two conversion side lines are connected with the low voltage side pipe arrangement, and will with respect to above-mentioned main valve seat on above-mentioned axial direction slidably main valve plug dispose with above-mentioned piston with being connected, by high-pressure refrigerant being imported the either party of above-mentioned two secondary valve chambers, and the secondary valve chamber of the opposing party is reduced pressure, thereby utilizing in this post-decompression secondary valve chamber makes above-mentioned piston and main valve plug to this pair valve chamber side shifting with the interior differential pressure of above-mentioned main valve chamber, and the recess that utilizes this main valve plug make above-mentioned low voltage side pipe arrangement select a ground with above-mentioned two the conversion side lines either party be communicated with, and be communicated with above-mentioned high pressure side pipe arrangement by the conversion side line of above-mentioned main valve chamber with the opposing party, with flowing of conversion refrigeration agent, this runner changing valve is characterised in that
Form auxiliary-seat portion at the two ends of above-mentioned valve casing inside, this auxiliary-seat portion is side-prominent to above-mentioned main valve chamber, and the pump drainage gas passage that makes the passage that becomes above-mentioned refrigeration agent is to the valve casing inner opening,
On above-mentioned each piston and with above-mentioned auxiliary-seat portion corresponding above-mentioned axis on form the equal pressure passageway that above-mentioned main valve chamber and above-mentioned secondary valve chamber are communicated with, and in this equal pressure passageway, set secondary valve, utilize this pair valve to change the conducting and the obturation of this equal pressure passageway moving of above-mentioned axial direction with respect to this equal pressure passageway
At above-mentioned piston when above-mentioned post-decompression secondary valve chamber side shifting finishes, the above-mentioned secondary valve obturation of this piston should pair valve chamber side the opening of above-mentioned auxiliary-seat portion, thereby and pass through this auxiliary-seat portion and the above-mentioned equal pressure passageway of this pair valve butt conducting, and make above-mentioned post-decompression secondary valve chamber and above-mentioned main valve chamber reach all pressures by means of this equal pressure passageway.
2. runner changing valve according to claim 1 is characterized in that,
Above-mentioned piston has the liner that contacts with the inner face of above-mentioned valve casing, form the rake that extends with ring-type to the central part side of valve casing in the periphery of this liner, this rake for its sectional shape along move closer to the shape that tilts in the direction of the inner face of valve casing along with central part towards above-mentioned valve casing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-112976 | 2010-05-17 | ||
| JP2010112976A JP5080612B2 (en) | 2010-05-17 | 2010-05-17 | Flow path switching valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102252114A true CN102252114A (en) | 2011-11-23 |
| CN102252114B CN102252114B (en) | 2013-02-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
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| CN2011101091837A Active CN102252114B (en) | 2010-05-17 | 2011-04-25 | Flow path switching valve |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2388541B1 (en) |
| JP (1) | JP5080612B2 (en) |
| CN (1) | CN102252114B (en) |
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| CN105402439A (en) * | 2014-09-10 | 2016-03-16 | 株式会社鹭宫制作所 | Slide valve and refrigeration circulation |
| CN105937648A (en) * | 2015-03-06 | 2016-09-14 | 株式会社鹭宫制作所 | Slide valve and refrigeration cycle |
| CN106286891A (en) * | 2015-05-15 | 2017-01-04 | 浙江盾安人工环境股份有限公司 | Combined electromagnetic switching valve and air conditioning system thereof |
| CN113167396A (en) * | 2018-11-29 | 2021-07-23 | 株式会社不二工机 | Flow path switching valve |
| JP2022187857A (en) * | 2021-06-08 | 2022-12-20 | 株式会社不二工機 | Channel switch valve |
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| JP6478585B2 (en) * | 2014-11-26 | 2019-03-06 | 株式会社不二工機 | Flow path switching valve |
| JP6478586B2 (en) * | 2014-11-26 | 2019-03-06 | 株式会社不二工機 | Flow path switching valve |
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| JP7137834B2 (en) * | 2018-09-18 | 2022-09-15 | 株式会社不二工機 | four-way switching valve |
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| CN105402439A (en) * | 2014-09-10 | 2016-03-16 | 株式会社鹭宫制作所 | Slide valve and refrigeration circulation |
| CN105402439B (en) * | 2014-09-10 | 2018-08-28 | 株式会社鹭宫制作所 | Guiding valve and freeze cycle |
| CN105937648A (en) * | 2015-03-06 | 2016-09-14 | 株式会社鹭宫制作所 | Slide valve and refrigeration cycle |
| CN105937648B (en) * | 2015-03-06 | 2019-06-18 | 株式会社鹭宫制作所 | Slide valve and refrigerating cycle |
| CN106286891A (en) * | 2015-05-15 | 2017-01-04 | 浙江盾安人工环境股份有限公司 | Combined electromagnetic switching valve and air conditioning system thereof |
| CN106286891B (en) * | 2015-05-15 | 2019-06-11 | 浙江盾安人工环境股份有限公司 | Combined electromagnetic switching valve and its air-conditioning system |
| CN113167396A (en) * | 2018-11-29 | 2021-07-23 | 株式会社不二工机 | Flow path switching valve |
| JP2022187857A (en) * | 2021-06-08 | 2022-12-20 | 株式会社不二工機 | Channel switch valve |
| JP7280631B2 (en) | 2021-06-08 | 2023-05-24 | 株式会社不二工機 | Flow switching valve |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2388541A3 (en) | 2015-04-29 |
| CN102252114B (en) | 2013-02-13 |
| EP2388541A2 (en) | 2011-11-23 |
| JP5080612B2 (en) | 2012-11-21 |
| EP2388541B1 (en) | 2016-07-06 |
| JP2011241870A (en) | 2011-12-01 |
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